Variable platen feed mechanism



March l5, 1932. LAST 1,849,494

VARIABLE PLATEN FEED MECHANISM Filed July 16, 1926 6 Sheets-Sheet 2March 15, 1932. J. LAST 1,849,494

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attenua! Patented Mar. 15, 1932 l UNITED STATES PATENT OFFICE IAMESLAST, 0F KINGSTON, PENNSYLVANIA, A SSIGNOR, BY MESNE ASSIGNMENTS, T0REMINGTON RAN D INC., 0F NEW YORK, N. Y., A CORPORATION OF DELAWAREVARIABLE PLATEN FEED MECHANISM Application led July 16,

The present invention relates to a paper feed mechanism and moreparticularly to a variable feed for the platen of such a mechanism.

Some of the objects of the present invention are to provide an improvedmechanism for controlling the line spacing of printing and recordingmechanisms, such as employed with adding, calculating, tabulating andother machines wherein paper feed takes place for the proper listing ofitems and totals; to provide a feeding mechanism for a platen wherebyperiodic changes in the line spacing automatically take place; toprovide means for varying the line spacin of a platen at will; toprovide a paper ceding mechanism actuated by the release of prestoredenergy while the degree of feed is determined by the automaticinterposition of appropriate stops; to provide an automatic control forline spacing whereby a feed of any selected number of minimumline-spaces takes place between successive printing or recordingstrokes, such number of selected line-spaces being less than thatselected for alternate total strokes; to provide an automatic controlfor line spacing whereby after the lirst and alternately occurring totalstrokes a feed of any selected number of line spaces takes place, suchnumber being less than that selected for the other alternate totalstrokes; to provide an automatic control for line spacing whereby thefeed for total strokes, alternating Cwith those last above referred to,have any selected number of line-spaces within the capacity of theapparatus; and to provide other improvements as will hereinafter appear.

In the accompanying drawings, Fig. 1 represents a side elevation, withthe left hand pivot plate removed, of one form of the present inventionas applied to the platen drive of a tabulating machine; Fig. 2represents a sectional elevation on line 2-2 of F ig. 1; Fig. 3represents a part sectional v plan .with the rim cover removed; Fig. 4

represents a section on line 4-4 of Fig. 2; Fig. 5 represents a sectionon line 5-5 of Fig. 2; Fig. 6 represents a section on line 6 6 of Fig.2; Fig. 7 represents a section 1926. Serial No. 122,925.

on line 7-7 of Fig. 2; Fig. 8 represents a section on line 8-8 of Fig.2; and Fig. 9 represents a section on line 9-9 of Fig. 2.

Referring to the drawings, one form of the present invention is shown asapplied to the control of line spacing of aplaten 10, (Fig. 2), of atabulating machine, the platen 10 being mounted upon a platen spindle11, which latter is controlled in its rotary movement by the mechanismof the present invention.

For actuating the spindle 11, it is provided with a ratchet wheel 12-7(Figs. 2 and 4), and two control ratchet wheels 13 and 14, all of saidratchet wheels being keyed or otherwise made fast to the spindle 11. Thewheels 12- and 13 are shown pinned together in Figure 2. Motion istransmitted to the ratchet wheel 12 by a pawl 15 mounted upon an armsecured to a side of a pinion 16 which is freely rotatable about thespindle 11 and meshes with a drive gear sector 17, (Figs. 1 and 2),mounted for rocking movement about a pivot 18 supported by the frame orother fixed part. The gear sector 17 is arranged to be rocked on itsworking stroke by the load of a spring 19 stretched between a xed pin 20and a pin 21 which is fast to and projects from the side of the sector17, While the non-working stroke of the gear sector 17 takes place bythe engagement of one arm 22 of a bell crank 23 with the pin 21. Thebell crank 23 is, preferably, pivoted upon the pivot 18 and has itsother arm in the path of movement of a pin 24 projecting from an arm 25of a bell crank 26 which is keyed or ot-herwise made fast to the mainshaft 27 of the machine. The other arm 28 of the bell crank 26 isarranged to transmit motion to certain parts to carry out steps in thecycle of operations as will hereinafter be explained in detail. Sincethe ratchet wheel 13 serves to locate the stopping position of theratchet wheel 12, its teeth are arranged opposite with respect to theteeth of the ratchet wheel 12, (Figs. 4, 5 and 6), and a check pawl 3()is pivotally mounted `upon a rod 31 in the plane of the Wheel 13 andwith which it is held in engagement by the load of a spring 32, (Fig.y5). .When the ratchet wheel 12 is being operated by the gear sector 17on the paper feed stroke because of the load of the spring 19, the checkpawl 30 is held out of the teeth of the control ratchet wheel 13 but isautomatically released so that the platen spindle comes to rest at theend of the predetermined line space or spaces.

. For controlling and varying the travel of the platen spindle 11, a.drum 33, (Figs. 2,6, 7, 8 and 9), is co-axially arranged about theplaten spindle 11 being rotatably supported at one end upon a boss 34,(Fig. 2), of a head 35, which is fixed to the frame, and at the otherend being connected to a boss 36, which is freely rotatable upon thespindle 11 and carries an arm 37. The drum 33 carries, as partsadjustably connected to it, three cam rings 40, 41 and 42, (Figs. 2, 7,8 and 9), all of these parts being frictionally clamped together bymeans of a nut 44 which 1s threaded upon one end of the drum 33. .Theopposite end of the drum 33 is also provided with an arm 45, (Figs. 2and 6), projected radially therefrom and serving a purpose to bepresently described. A torsion spring 46 is located within the drum 33having one end secured to the fixed boss 34 and its opposite endconnected to the drum 33, while suitably spaced from this spring 46 is asecond torsion spring 47, preferably of lighter construction, one end ofwhich is fast to the boss 34 and the opposite end of which is fast tothe boss 36 of the movable arm 37. Considering rst the control of theratchet wheel 13 for line spacing without regard to total operations,such control takes place through the rotation of the ring 40 and its camnotch 48, (Fig 7). 1n conjunction with the ratchet wheel 43 and theparts controlled thereby. The release of the drum 33 to the action ofthe torsion spring 46 is effected by a setting pawl 50, (Fig. 6),secured to a short shaft 51 pivotedin the arm 37, and meshing with thecontrol ratchet wheel 14 while its nose 52 is in position to be engagedby a latch 53 pivoted to the arm 45 and held pressed toward the settingpawl by a coil spring 54 stretched between a pin on the latch 53 and anarm keyed to the short shaft 51. The spring 54 urges the setting pawl torock into the position shown. As long as the nose 52 engages the controlratchet wheel 14, there is no movement of the drum 33, so in order torelease the setting pawl 50 for such movement, it is provided with anintegral tail piece 55 having a lug 56 which is in the path of movementof a trip finger 57. This finger 57 is pivoted to one arm of a three armbell crank 58, which is fast to a rock shaft 59 and has another armwhich serves to interconnect the trip finger 57 with a coil spring 60,while another coil spring 61 is stretched between the aforesaid arm anda. fixed point 62. The third arm 63 of the bell crank 58 extends intothe path of movement of a pin 64 projecting from a bell crank 65, whichis pivoted at 66, and has its opposite arm joined to a shoulder screw 67(Fig. l), by which it is pivotally connected to a link 68, and also to abar pawl 70. A lever cam 69 is swung from the pivot 66 and connects atits lower extremity to the arm 28 by a pin 71 riding in a cam slot 72,and also carries a laterally disposed pin 73 which is arranged to movein a path to engage the bar pawl so that a shoulder 74 of the4 said barpawl 70 is removed from a'holding pin 75 to thereby release the pawl 70to the action of an operating spring 76.

The trip finger 57, (Figs. 5 and 6), is also arranged to control thelifting of the check pawl 30 by the provisionl of a step 77 whichco-acts at a predetermined time with a stud 78 on the check pawl 30.Adjacent to the check pawl 30 there is a pivoted check latch 8O undercontrol of a spring 8l and having a notch 82 so positioned as to receivea pin 83 of the pawl 30 when the latter is in its unlatched position.The check latch has an extended tail piece 84 so arranged as to be inthe path of movement of the lug 56 upon the setting pawl 50 on thearrival of the ratchet wheel 14 with the setting pawl re-engaged, toeffect re-engagement of the check pawl 30 due to the resultingdisengagement of the check latch 80. f

For the purpose of bringing the drum 33 to rest in the positiondetermined by the cam notch 48 in the cam ring 40', a cam lever 85,(Fig. 7), is provided, the same being pivoted upon the rod 31 and havingits nose 86 arranged to drop into the cam notch 48 because of the loadof a spring 87 which is stretched to a fixed pin 88 as will be apparent.This cam lever has a rearwardly disposed tail 90 arranged to transmitits movement through a bridge pin 91 to a limit pawl 92, also pivoted onthe rod 3l and having its nose 93 in the plane of the ratchet wheel 43but in inoperative position being held out of said engagement by therelatively weaker spring 94 also stretched to the pin 88. The cam lever85 is also provided with a finger 95 and a cam shoulder 96 for purposesrespectively to be described. Thus when the drum 33 is released to theaction of the torsion spring 46 it can only turn until the cam notch 48registers with the nose 86 of the cam lever 85 because the latter thenswings under the action of the spring 87, and this swinging movement istransmitted by the tail 90 to the bridge pin 91 to swing the limit pawl92 against the tension of the spring 94 so that the pawl nose 93 engagesthe ratchet wheel 43 which is fast to the drum 33.

When the automatic action requires a line spacing different from thatdetermined by the cam ring 40, it is necessary to provide a means forholding the cam lever 85 from movement when its nose 86 comes intoregister with the cam notch 48. This is accomplished by providing an arm97 fixed to the rock shaft 59 and having a shoulder 98 movable in a pathto pick up the finger 95 and thereby rock the cam lever 85 to a positionwhere its cam shoulder 96 falls under the latch 100 of a latch arm 101,which is pivoted to a rod 102 and drawn to latching position by a spring103. The end of the latch arm 101 is spaced from and terminates in thepath of movement of the bridge pin 91 in order that it can move intolatching position without displacing the bridge pin 91 and beautomatically unlatched at the proper time by the movement of suchbridge pin 91 as the pawl 92 engages the ratchet 43 under control of camrings selected by a tot-al control means.

Under one total taking cycle, variation of .v the line spacing iscontrolled by the cam ring 41 (Fig.v 8) provided with a cam notch 104which is located for the proper line spacing by angularly turning thering 41 so that the notch 104 is spaced the desired angular distancefrom the notch 48 in the cam ring 40 to give the additional platentravel, and in which position it is locked by the nut 44 as previouslyexplained. l When this cam ring 41 controls the line spacing,-the drum33 is brought to rest by the limit pawl 92 as before, but in thisinstance its movement is governed by a cam lever 105 pivoted upon thelrod 31 and having its nose 106 in position to drop into the notch 104under the action of a spring 107 stretched to the pin 88. This cam lever105 also hasaprojectingtail piece 108 engarring the lower side of thebridge pin 91, en 1ikewiee ii ie provided with e ieieh shoulder 110 sothat it can be held out of engagement with the cam ring 41 by seatingback of a latch 111 on a latch arm 112, the latter being pivoted to therod 102 and pulled to latching position by the spring 113. The latch arm112 terminates in the path ofmovement of the bridge pin 91 in order thatit can be shifted at the proper time to unlock the cam lever 105. Theend of the latch arm 112 is spaced from the bridge pin to permit thelatch to emerge the latch shoulder 110 without depressing the bridge pin91. In order to swing the cam lever 105 in the direction to be latchedby the arm 112, it carries a pivot screw 114 to form a support for apawl 115 arranged to be shifted by a spring 116 to operative positionbut held in inoperative position by means of a latch 117 which is freelymovable upon the rock shaft 59. The latch 117 seats in a shoulder 118 ofthe pawl 115, and is automatically disengaged by a pin 120 projectingfrom the side of the arm 97 at the proper location. The opposite end ofthe pawl 115 is provided with a step 121 in order to coact with a stop122 projecting laterally from the arm 97 whereby latching of the camlever 105 is achieved by the latch 111 of the latch lever 112 andcontrol of the drum 33 is transferred to Vanother part, in this instancethe cam ring 42. The means for operating the arm 97 from the totalcontrol shaft 1150 latch the pawls 85 and 105 will be described ater.

Under total taking cycles alternating with the above mentioned totaltaking cycle, the cam ring 42, (Fig. 9), automatically comes into actionbecause the two cam rings 40 and 41 have become ineifective through thelatching out of their respective cam levers and in consequence a camnotch 123 in the cam ring 42 becomes the controlling factor. This notch123 is located a greater angular distance from the rotational startingpoint of the drum 33 than either of the notches 48 and 104, andtheangular distance between the cam notch 123 and the cam notch 104represents the increase of line spacing over the line spacing ascontrolled by the cam ring 41. The rest position of the drum 33 iscontrolled by the cam ring 42 as determined by a third cam lever 124which has its nose 125 in the plane of the ring 42 and projected towardsuch ring by a spring 126 stretched to the pin 88 whereby the nose ofthe"cam lever drops into the notch 123 when the two parts are broughtinto register. The cam lever 124 is pivoted upon the rodn 31 and has arearwardly extending tail piece 127 resting against the bridge pin 91.When, therefore, the cam ring 42 reaches the position where the notch123 is opposite the nos-e 125, the cam lever 124 is rocked by its spring126 and transmits movement through the bridge pin 91 to the limit pawl92 which is thus brought into rocking engagement with the ratchet 43 tohold the drum 33 against further movement.

.This movement of the bridge pin 91 lifts the latch arms 101 and 112 torelease the pawls 85 and 105. l

For bringing the cam rings 41 and 42 into operation during a totaltaking cycle, the total control shaft 128, (Fig. 1), is provided with afiXedly mounted arm 130 which carries the holding pin 75, heretoforereferred to, and which is in engagement with the shoulder 74 upon thebar pawl 70 whereby the latter is shifted in the direction of the arrowH. When the bar pawl is released from the holding pin by the laterallypushing movement of the pin 73, the bar pawl 70 then l moves in thedirection of the arrow F.

For restoring the bar pawl at the end of the out stroke of the mainshaft 27, a pin 131 is fixed to the bar pawl 70 in a position to beengaged by the end of an arm 132 of a bell crank 133, which is freelyrotatable upon the total shaft 128 and is arranged to be rocked by a pin134 on the other arm of the bell crank 133, said pin 134 being locatedin the path of movement of a lug 135 upon the arm 28. i

The relatching of the shoulder 74 with the holding pin 75 is effected atthe end of each cycle by the pin 71 coacting with the end of a slot 136located in the link 68 which is jointed to the bell crank 65 by means ofthe shoulder screws 67.

The operation of 'v the mechanism is as follows:

The parts are shown, in Fig. 1, in the resting position, and during theout-stroke of the machine, the main shaft 27 rotates so as to rock thebell crank26 in the direction of the arrow C and so to drive by means ofthe pin 24 the bell crank 23 in the direction of the arrow D so that thearm 22 of the bell crank 23 engages the pin 21 in the drive sector 17rotating it about the pivot 18, which is common to the sector 17 and thebell crank 23, and thereby extends the spring 19 thus storing the energyrequired for the subsequent driving of the platen 10. On this strokealso the sector 17 rotates the pinion 16 freely about the spindle 11 ofthe platen 10 in the direction of the arrow E trailing the drive pawl15, (Fig. 4), over the ratchet wheel 12 which is rigidly mounted on theplaten spindle 11. At the beginning of this same stroke, in addition,the pin 71 in the arm 28 of the bell crank 26 coacts with the cam slot72 in the arm 68, which is pivoted about the centre 66 of the bell crank65, so as to disengage, by means of the pin 73, the pawl 70, which isjointed by the shouldered screw 67 to the bell crank 65, from the pin 75in the arm 130 which is rigidly mounted on the existing total controlshaft 128. This disengagement allows the load resulting from the spring76 to move the pawl 70 in the direction of the arrow F so as to rotatethe bell crank 65 about its pivot 66 and further by means of the pin 64in the bell crank 65 to rotate the bell crank 58, (Figs. 5 and 6), androck shaft 59 in the direction of the arrow G against the action of theweaker spring 61 and so to cause the trip finger 57 to engage the lug 56in the setting pawl 50 allowving the latch 53 to be engaged with thenose 52 of the setting pawl 50 retaining it out of engagement with theratchet wheel 14 in order that the arm 37 which carries the setting pawl50 and is rigid with the boss 36, (Fig. 2), which is freely mounted onthe platen spindle 11, may now be rotated around the spindle 11 by thetorsion spring 46 which is anchored at one end to the fixed boss 34 andat the other to the drum 33 which carries the arm 45 bearing the latch53, relative movement between the arms 45 and being limited by the pin49 in the arm 45. The rotation of the arm 45 is checked on the arrivalof the notch 48 in the cam ring 40, (Fig. 7 which is variably clamped tothe drum 33 by the nut 44) at the nose 86 of t-he cam lever 85, the nose86 thereupon dropping into the notch 48 because of the load of thespring 87, the tail 90 of the lever 85 raising the bridge pin 91 in thelimit pawl 92 against the action of the spring 94, engaging the nose 93of the said limit pawl 92 with the ratchet wheel 43 and so/arresting therotation of the drum 33 on which the ratchet wheel 43 is rigidlymounted. This partial rotation ofthe drum 33 takes place as a result ofthe turning moment applied by the spring 46 which is so scaled that thepin 49 (Fig. 6) 1n the arm 45 which is rigid with the drum 33 maintainsa pressure against the arm 37 until the engagement of the limit pawl 92with the wheel 43 as has just been described. At this point the lighterspring 47, which is also anchored at one end to the fixed boss 34 butisanchored to the boss 36 of the arm 37 rotates the arm 37 4andconsequently withdraws the setting pawl 50 from the latch 53 on the arm45 so allowing the offset portion of the nose 52 of the pawl 50 tore-engage with the ratchet wheel 14 fiXedly mounted on the platenspindle 11. The aforesaid torsion springs 46 and 47 are of suchdimensions that the above functions are completed before the arrival ofthe lug 135, (Fig. 1), at the pin 134 in the bell crank 133 which isfreely pivoted on the total control shaft 128. The depression of the pin134 in the bell crank 133 by the lug 135 of the bell crank 26 at the endof the out-stroke of the main shaft 27 is such that the upper end of thearm 132 of the bell crank 133 engages with the pin 131 in the pawl 70and by drivin the pawl 70 in the direction of the arrow restores thebell crank 65 to the positlon it occupied before the release of the pawl7 0 from the pin by the co-action of the pin 71 with cam slot 72. Thisrestoration of the bell crank allows the spring 61, (Figs. 5 and 6), towithdraw the trip finger 57 so that its step 77, which at thecommencement of the cycle was prevented by the lug 56 from engagementwith the stud 78 in the check pawl 30, now engages with the said stud 78so that on the commencement of the return stroke of the main shaft 27the lug 135 on withdrawing from the pin 134 again allows the pawl 70 tomove in the'direction of the arrow F (the form of the cam slot 72 beingsuch that the shoulder 74 is maintained out of alignment with the pin75) so that the spring 76, overcoming the spring 6l, through the bellcrank 65, the pin 64, the bell crank 58 and the trip finger 57, causesthe step 77 to bear against the stud 78 and so to rotate the check pawl30 about its rod 31 to withdraw its nose from the ratchet wheel 13 whichis iXedly mounted on the platen spindle 11, the notch 82 of thecheck'latch 80 engaging with the pin 83 in the check pawl 30 andretaining the check pawl 30 disengaged from the ratchet wheel 13, therotation of the arm 37 as previously described having withdrawn the lug56 from the tail piece 84 of thel check latch 80. leaving it free tofunction as just set forth. The commencement of the return stroke of theshaft 27 also results in the withdrawal of the pin 24 in the bell crank26 from the bell crank 23 so that the spring 19 is now free to apply aturning moment through the sector 17, the pinion 16, the pawl 15 and theratchet Aso wheel 12 to the platen spindle 11. The disengagement of thecheck pawl 30 from the ratchet wheel 13 in the manner just describedallows this turning movement' to operate and rotate the platen spindle11 in the direction ofthe arrow K until the ratchet wheel 14, iixedl'vmounted thereon, by its engagement with the setting pawl 50 rotates thearm 37 in its return direction as indicated by the arrow K until the lug56 again engages with the tail piece 84 of the check latch 80 anddisengages the notch 82 from the pin 83 so allowing the check pawl 30 tore-engage with the ratchet wheel 1.3, terminating the rotation of theplaten spindle 11 in the direction for feeding the paper. Now if beforethe main shaft 27 commences its out-stroke the total shaft 128 should bepartially rotated in the direction of the arrow L (for the purpose ofsetting the machine to print a total) the pin being engaged with theshoulder 74 of the pawl 70 will move the pawl 70'in the direction of thearrow H, beyond its usual resting position, further extending the spring76 and withdrawing the pin'64 from the bell crank 58 so that the spring61 rotates the bell crank 58 and the pivot 59` causing the detent 97(Fig. 7), to rotate in the direction of the arrow M so as to lift thecam lever 85 from the surface of the cam ring 40 and to cause the camlever 85 to be latched by the latch 100 in a disengaged position.

The ensuing machine cycle will now cause the parts to function as beforewith the exception that the limit pawl 92 will be. engaged with theratchet wheel 43 by its bridge pin 91 being lifted by the tail of thecam lever 105, (Fig. 8) whose co-action with the cam ring 41 is exactlysimilar to that of the cam lever 85 with the cam ring 40. The increasedlength of feed is obtained by setting the notch 1404 at an angulardistance in the direction of the arrow N from the notch 48 in the camring 40. It. should be understood that the engagement of the limit pawl92 effects the disengagement of all latches such as 100 and therefore,that the increased length of feed is only given when the total controlshaft 128 has first been operated. Therefore, the cycles between thosebefore which the total control shaft 128 is operated will only result inthe feed controlled by the co-action of the cam ring 40 and cam lever85.

In order that the total taking cycle, following that total taking cyclein which the feed is controlled by the co-action of the cam ring 41 andthe cam lever 105I` may result in a feed of greater'length than thatprovided by such co-action, the iirst rotation of the pivot 59 in thedirection of the arrow M, (Fig. 7), causes the pin 120, (Fig. 8) ,todisengagethelatch117 from the shoulder 118 of the pawl 115 so that thepawl 115 assumes the posit`on shown vby the dott-ed lines, its step 121p ssing to a position resting against the stud 122 in the detent 97 sothat its shoulder 118 passes below the nose of the latch 117 with theresult that, on the disengagement of the shoulder 74 in the bar pawl 70from the pin 7 5, the latch described by the detent 97 and the lever 105byI the stud 122, the pawl 115 and pivot screw 114. the upliftedposition of which, due to the latching of the lever 105, maintaining thepawl 115 sufficiently raised for the latch 117 v to re-engage with theshoulder 118 on the return stroke of the rock shaft 59 cons uent on thedisengagement of the shoulder 4 in the bar pawl 7 0 from the pin 75, atthe commencement of the out-stroke of the main shaft 27. The engagementof the limit pawl 92 with the ratchet wheel 43 is now effected by thethird cam lever 124 which co-acts with the cam ring 42 which is set soas to give a longer feed than either the cam ring 41 or the cam ring 40.The movement of the bridge pin releases the latch arms 101 and 112 sothat on the next ensuing cycle, the line spacing will be controlled bythe cam ring 40 if an adding operation is performed, -or by the cam ring41 if a total taking operation is performed.

The said cam rings are released or clamped simultaneously on the manualoperation of the nut 44 and when free may be conveniently rotated to thedesired adjustments by finger operation.

The relatching of the shoulder 74 of the bar pawl 70 on the pin 75 iseffected at the end of each cycle by the pin 71 co-acting with the endof the slot 136 in the link 137 also jointed to the bell crank 65 by theshoulder screw 67.

It will now be apparent that a complete unitary platen mechanism forfeeding paper has been devised wherein the stored energy serves as theactuating medium for advancing the platen step-by-step to give thedesired line spacing. By the present invention uniform line spacing canbe obtained or periodically the line spacing can be automatically variedas when totals are taken in an adding machine or for any other purpose.Furthermore, the platen feed is under positive control which gives exactspacing and eliminates over-run of the platen. Also by the employment ofa plurality of line-spacing controls any desired line-spacing effectscan be automatically provided for, and while in the present embodimentof the invention only two such controls are shown, it is to beunderstood the invention is not limited in this respect.

While only a single form is shown in which this invention may beembodied, it is to be understood that the invention is notI limitedAating means.

2. A platen feed mechanism comprising a platen, means for actuating saidplaten to cause predetermined line spacing, and means controlled by thetotal operating mechanism of an adding machine for causing two differentvariations of said line spacing.

3. A platen feed mechanism comprising a platen, means for actuating saidplaten to cause predetermined line spacing, means for causing twodifferent variations of said line spacing, and means controlled by thetotalv operating mechanism of an adding machine for selectivelyoperating said causing means.

4. A platen feed mechanism comprising a platen, means for actuating saidplaten to cause predetermined line spacing, means for causing twodiHerent variations of said line spacing, and means controlled by thetotal operating mechanism of an adding machine for alternately operatingsaid causing means.

5. A platen feed mechanism comprising a platen, means for moving saidplaten to cause a predetermined line spacing, means periodicallyoperative to automatically increase the movement of said platen toproduce a line spacing greater than said predetermined line spacing, andmeans also periodically operative to automatically increase the movementof said pla-ten to produce a line spacing greater than either of saidplaten movements.

6. A platen feed mechanism comprising a platen, means for moving saidplaten to cause apredetermined line spacing, means periodicallyoperative to automatically increase the movement of said platen toproduce a line spacing greater than said predetermined line spacing,means valso periodically operative to automatically increase themovement of said platen to produce a line spacing greater than either ofsaid platen movements, and means selectively operating said periodicallyoperating means.

7. In a platen feed mechanism, the combination of a platen, an addingmachine shaft, and a total control shaft, means for moving said platento produce a series of equal line spaces, connections between saidadding machine shaft and said control for actuating said moving means,means actuated by said total operating shaft for preventing said movingmeans from further effecting equal line spacing, and means valsoactuated by said total control shaft for causing said moving means tovary said line spacing.

8. In a platen feed mechanism, the combination of a platen, an addingmachine shaft,

and a total control shaft, means for moving said platen to produce aseries of equal line spaces, connections between said adding machineshaft and said control for actuating said moving'means, means actuatedby said total operating shaft for preventing said moving means fromfurther effecting equal line spacing, and means also actuated by saidtotal control shaft for causing said moving means to increase said linespacing.

9. In a platen feed mechanism, the combination of a platen, an addingmachine shaft, and a total control shaft, means for moving said platento produce a series of equal line spaces, connections between saidadding machine shaft and said control for actuating said moving means,means actuated by said total operating shaft for preventing said movingmeans from further effecting equal line spacing, means also actuated bysaid total control shaft for causing said moving means to increase saidline spacing, and means for automatically causing said moving means toresumeeffecting equal line spacing.

10. In a platen feed mechanism, the combination of a platen, an addingmachine shaft, and a total controlshaft, means for moving said platen toproduce a series of equal line spaces, connections between said addingmachine shaft and said control for actuating said moving means, meansactuated by said total operating shaft for preventing said moving meansfrom further effecting equal line spacing, means also actuated by saidtotal control shaft for causing said moving means to vary said linespacing, and means for automatically causing said moving means t0 resumeeffecting equal line spacing.

11. A platen feed mechanismcomprising a platen shaft, devices for movingsaid shaft a predetermined angular distance to produce uniform linespacing, a ratchet fast to said platen shaft, a drum mounted to moverelatively about said platen shaft, -a torsional spring arranged toactuate said drum, means actuated by said drum for controlling themovement of said ratchet, andmeans for automatically varying the throwof said drum.

12. A platen feed mechanism comprising a platen shaft, devices formoving saidshaft a predetermined angular distance to produce uniformline spacing, a ratchet fast to said platen shaft, a drum mounted tomove relatively about said platen shaft, a torsional spring arranged toactuate said drum, means 13. A platen feed mechanism comprising a platenshaft, devices for moving said shaft a predetermined angular distance toproduce uniform line spacing, a ratchet fast to said platen shaft, adrum mounted to move relatively about said platen shaft, a torsionalspring arranged to actuate said drum, means actuated by said drum forcontroling the movement of said ratchet, separate mechanisms forcontrolling the throw of said drum, each of said mechanisms producing adifferent throw and including a settable adjustment for throw variation,and means for automatically selecting said mechanisms.

14. A platen feed mechanism comprising a platen shaft, devices formoving said shaft a predetermined angular distance to produce uniformline spacing, a ratchet fast to said platen shaft, a drum mounted tomove relative about said platen shaft, a torsional spring arranged toactuate said drum, means actuated by said drum for controlling themovement of said ratchet, separate mechanisms for controlling the throwof said drum, each of said mechanisms producing a. different throw, andmeans for causing said mechanisms to function in sequence.

15. A platen feed mechanism comprising a platen shaft, devices formoving said shaft a predetermined angular distance to produce uniformline spacing, a ratchet fast to said platen shaft, a drum mounted tomove relatively about said platen shaft, a torsional spring arranged toactuate said drum, means actuated by said drum for controlling themovement of said ratchet, separate mechanisms for controlling the throwof said drum, each of said mechanisms producing a different throw, andmeans for causing said mechanisms to function periodically.

16. A platen feed mechanism comprising a platen shaft, devices formoving said shaft a predetermined angular distance to produce uniformline spacing, a ratchet fast t0 said platen shaft, a drum mounted tomove relatively about said platen shaft, a torsional spring arranged toactuate said drum, means actuated by said drum for controlling themovement of said ratchet, separate'mechanisms for controlling the throwof said drum, each of said mechanism producing a different throw, andmeans for causing said mechanisms to function periodically andalternately.

17. In a platen feed mechanism, the combination of a platen shaft, anadding machine shaft, and a total control shaft, a ratchet fast to saidplaten shaft, a drum mounted to rotatel about said platen shaft,` atorsional spring arranged to actuate said drum, means actuated by saiddrum for controlling the movement of said ratchet, means actuated bysaid adding machine shaft for controlling the release of said drum,separate mechanisms for controlling the throw of said drum, each of saidmechanisms producing a different throw, and means actuated by said totalcontrol shaft for automatically selecting said mechanism.

18. In a platen feed mechanism, the combination of a platen shaft, anadding machine shaft, and a total control shaft, a ratchet fast to saidplaten shaft, a drum mounted to rotate about said platen shaft, atorsional spring arranged to actuate said drum, means actuated bv saiddrum for controlling the movement of said ratchet, means actuated bysaid adding machine shaft for controlling the release of said drum,separate mechanisms for controlling the throw of said drum, each of saidmechanisms producing a different throw, and means actuated by said totalcontrol shaft for causing said mechanisms to function in sequence.

19. In a platen feed mechanism, the combination of a platen shaft, anadding machine shaft, and a total control shaft, a ratchet fast to saidplaten shaft, a drum mounted to rotate about said platen shaft. atorsional spring arranged to actuate said drum, means actuated by saiddrum for controlling the movement of said ratchet, means actuated bysaid adding machine shaft for controlling the release of said drum,separate mechanisms for controlling the throw of said drum, each of saidmechanisms producing a different throw, and means actuated by said totalcontrol shaft for causing said mechanisms to function periodically.

20. A platen feed mechanism comprising a platen shaft, devices formoving said shaft a predetermined angular distance to produce uniformline spacing, a ratchet fast to said platen shaft, a drum mounted tomove relatively about said platen shaft, a torsional spring arranged toactuate said drum, means' actuated byl said drum for controlling themovement of said ratchet, separate mechanisms for controlling the throwof said drum, each of said mechanisms producing a different throw, andincluding a settable adjustment for throwing variation, and means forcausing said mechanisms to function in sequence.

21. A platen feed mechanism comprising a platen shaft, devices formoving said shaft a predetermined angular distance to produce uniformline spacing, a ratchet fast to said platen shaft, a drum mounted tomove relatively about said platen shaft, a torsional spring arranged toactuate said drum, means actuated by said drum for controlling themovement of said ratchet, separate mechanisms for controlling the throwofsaid drum, eachofsaidmechanismsproducing a different throw, andincluding a settable adjustment for throwing variation, and means forcausing said mechanisms to function periodically.

22. A, platen feed mechanism comprising a platen, means for actuatingsaid platen to cause predetermined line spacing, a plurality of controlsfor respectively varying said line spacing means, and means forautomatically making a selection of said controls for causing apredetermined variation of said line spacing.

23. A platen feed mechanism comprising a platen, means operated bystored energy for actuating said platen to cause predetermined linespacing, a plurality of controls for respectively varying said linespacing means, and means for automatically making a selection of saidcontrols for causing a predetermined variation of said line spacing.

24. A platen feed mechanism comprising a platen, means for actuatingsaidplaten to cause predetermined line spacing, and means automaticallyadjusted before each platen feeding cycle to register the predetermineddimension of line spacing.

25. A platen feed mechanism comprising a platen, means for actuatingsaid platen to cause predetermined line spacing, means automaticallyadjusted before each platen feeding cycle to register the predetermineddimension of line spacing, and means positively limiting saidadjustment.

26. A platen feed mechanism comprising a platen, means for actuatingsaid platen to cause predetermined line spacing, means automaticallyadjusted before each platen feeding cycle to register the predetermineddimension of line spacing, means positively limiting said adjustment,and means controlled by said registering means for positivelydetermining the dimension of the ensuing line spacing.

27. A platen feed mechanism comprising a platen, means for actuatingsaid platen to cause predetermined line spacing, means automaticallyadjusted before each platen feeding cycle to register the predetermineddimension of line spacing, means positively limiting said adjustment,means controlled by said registering means for positively determiningthe dimension of the ensuing line spacing, and means including aplurality of selective controls for regulating the dimension of suchpreadjustment.

28. A platen feed mechanism comprising a platen, means for actuatingsaid platen to cause predetermined line spacing, and means selectivelyautomatically operative to cause a plurality of periodic variations ofsaid line spacing.

29. In combination with the paper feeding means of an adding and totaltaking machine, of means for varying the paper feed after the printingof a total, and means for varying the paper feed dierently after the jprinting of the next succeeding total.

30. A platen'feed mechanism comprising line-spacing means for actuatingthe platen, and controlling means for limiting the action of theline-spacing means to cause spacings of three predetermined widths, thecontrolling means comprising a device that is moved from an ineective toaneffective position in one operation of the machine and is actuatedwhen it functions in another operation of the machine.

3l. A platen feed mechanism comprising line-spacing means for actuatingthe platen, and controlling means for limiting the action of theline-spacing means to cause spacings of three predetermined widths, thecontrolling means comprising a device that is moved to effectiveposition in a total-taking operation and is actuated when it functionsin a succeeding operation of the machine.

32. A platen feed mechanism comprising line-spacing means for actuatingthe platen, and controlling means for limiting the action of theline-spacing means to cause spacings of three predetermined widths, thecontrolling means comprising mechanism the functional action of which iseffected in one operation of the machine and depends on two operationsof the machine.

33. A platen feed mechanism comprising 4line-spacing means for actuatingthe platen, and controlling means for limiting the action of theline-spacing means to cause spacings of three predetermined widths, thecontrolling means comprising mechanism the functional action of whichdepends on a total-taking operation and which functions in a succeedingoperation of the machine.

34. A platen feed mechanism comprising line-spacing means for actuatingthe platen, and controlling means for limiting the action oftheline-spacing means to cause spacings of three predetermined widths eachof which is variable, the controlling means comprising mechanism thefunctional action of which is effected in one operation of the machineand depends on two operations of the machine.

35. A platen feed mechanism comprising line-spacing means for actuatingthe. platen, and controlling means for limiting the action of theline-spacing means to cause spacings of three predetermined widths, thecontrolling means comprising two devices, one of which acts on the otherand to both of which motion is imparted in each of two operations of themachine and which jointly function in and only in the later operation.

36. A platen feed mechanism comprising line-spacing means for actuatingthe platen, and controlling means for varying the action ofi-heline-spacing means to cause spacings of different widths, thecontrolling means comprising mechanism the functional action of which iseffected in one operation of the machine and depends on two operationsof the machine.

Signed at Philadelphia, county of Philadelphia, State of Pennsylvania,this 14th day

